7.1 Parallelism Controls for Planar Surfaces & Cylindrical Features of Size

ASME GDTP Technologist Y14.5-2009

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1 Chapter 1: Scope, Certification Logistics, Fundamental Rules & General Dimensioning

1.1 ASME GDTP Technologist Exam Scope, Prometric Logistics, & Certification Rules 1.2 Fundamental Rules of ASME Y14.5-2009 (Rules a through p) 1.3 Engineering Drawing Standards, Drawing Units, & Basic vs. Toleranced Dimensions 1.4 Dimensioning Features: Diameters, Radii, Chamfers, Countersinks, Counterbores, Spotfaces, Keyseats & Slots 1.5 Application of Dimensions & Location of Features: Lines, Leaders, Reference Dimensions, Rectangular vs. Polar Coordinates

2 Chapter 2: Features, Limits of Size, & Material Condition Principles

2.1 Features, Features of Size, & Limits of Size 2.2 Rule #1 (Taylor Principle / Envelope Rule), Its Exceptions & Overrides 2.3 Material Condition Concepts: MMC, LMC, & RFS Calculations

3 Chapter 3: General Tolerancing & Symbology

3.1 Direct Tolerancing, Limit Dimensioning, & Angular Tolerancing 3.2 The 14 Geometric Characteristic Symbols, Feature Control Frames, & Special Modifiers 3.3 Screw Threads, Gears & Splines, Angular Surfaces, Tapers & Statistical Tolerancing 3.4 Feature Control Frame Placement, Combined Frames, Tolerance Zone Definition & Tabulated Tolerances

4 Chapter 4: Datum Reference Frames & Degrees of Freedom

4.1 Theoretical Datums, Datum Feature Simulators, & Physical Datum Features 4.2 Degrees of Freedom Constraint & The 3-2-1 Datum Precedence System 4.3 Planar, Cylindrical, & Width Datum Feature Establishment

5 Chapter 5: Advanced Datum Applications: Targets, Boundary Modifiers, Customized Frames & Restrained Condition

5.1 Datum Target Points, Lines, Areas, & Movable Datum Simulators 5.2 Material Boundary Modifiers (RMB, MMB, LMB) & Datum Shift Calculations 5.3 Functional Datum Feature Selection, Multiple Datum Reference Frames & Simultaneous vs. Separate Requirements 5.4 Rotational Constraint About a Datum Axis or Point & Customized Datum Reference Frames 5.5 Irregular & Complex Datum Features, Mathematically Defined Surfaces, Restrained Condition & Datum Feature Controls

6 Chapter 6: Form Tolerances

6.1 Flatness & Straightness Controls for Surfaces & Features of Size 6.2 Circularity & Cylindricity Controls, Differences, & Inspection

7 Chapter 7: Orientation Tolerances

7.1 Parallelism Controls for Planar Surfaces & Cylindrical Features of Size 7.2 Perpendicularity & Angularity Tolerances with Basic Angles & Tangent Plane

8 Chapter 8: Location: Position Fundamentals & Calculations

8.1 Position Tolerancing Fundamentals, True Position, & Coordinate Conversions 8.2 Bonus Tolerance & Virtual Condition Calculations for Internal & External Features 8.3 Projected Tolerance Zones (Ⓟ Modifier) & Fixed vs. Floating Fastener Formulas 8.4 Zero Positional and Orientation Tolerancing at MMC and at LMC 8.5 Surface vs. Axis Interpretation of Position & the Boundary Concept for Slots, Tabs & Noncircular Features

9 Chapter 9: Location: Patterns, Composite Controls, Coaxial & Symmetrical Relationships, and Functional Gaging

9.1 Hole & Slot Patterns, Multi-Segment Frames, & Composite Position Tolerancing 9.2 Functional Gaging Principles & Inspection Verification of Position 9.3 Coaxial Holes, Counterbored Holes, Non-Parallel Axes, Spherical Features & Bidirectional Position 9.4 Concentricity & Symmetry Tolerances Under ASME Y14.5-2009 9.5 LMC Applied to Position: Wall Thickness, Breakout Protection & Boundary Calculations

10 Chapter 10: Profile Tolerances

10.1 Profile of a Line & Profile of a Surface Fundamentals & Basic Geometry 10.2 Bilateral, Unilateral, & Unequally Disposed Profile Boundaries (Ⓤ Modifier) 10.3 Composite Profile Tolerances vs. Multiple Single-Segment Profile Controls 10.4 Profile Verification, Coplanarity Controls, & Non-Rigid Parts 10.5 Profile Applications: Conicity, Extruded and Irregular Shapes, and Profile-Controlled Datum Features 10.6 Modifier Rules for Profile & Combined Controls (Profile with Position, Orientation and Runout)

11 Chapter 11: Runout Tolerances & Comparative Control Analysis

11.1 Circular Runout vs. Total Runout Interpretation & Dial Indicator Verification 11.2 Comparative Analysis: Runout vs. Form, Orientation, & Concentricity Controls

7.1 Parallelism Controls for Planar Surfaces & Cylindrical Features of Size

Key Takeaways Explain This Topic AI

Parallelism (ASME Y14.5-2009 Section 6.4.2) is an orientation control defining a condition where a surface, centerplane, or axis is equidistant at all points from one or more datum planes or axes.

Orientation controls ALWAYS require at least one datum reference and NEVER control feature location; they govern angular tilt relative to datums while automatically refining form (flatness or straightness).

Planar surface parallelism establishes a 3D tolerance zone bounded by two parallel planes parallel to a datum plane, refines the Rule #1 size envelope, cannot exceed the size tolerance, and strictly prohibits material condition modifiers (Ⓜ or Ⓛ).

When applied to a feature of size (axis or centerplane), parallelism controls the derived median line or derived median plane, permits the Maximum Material Condition (Ⓜ) modifier, unlocks bonus tolerance, and establishes a fixed Virtual Condition boundary (MMC + tolerance for external features; MMC - tolerance for internal features).

Last updated: September 2026

7.1 Parallelism Controls for Planar Surfaces & Cylindrical Features of Size

Quick Answer: In ASME Y14.5-2009 , parallelism (Section 6.4.2) is an orientation control defining the condition of a surface, centerplane, or axis that is equidistant at all points from one or more datum planes or axes. Unlike form controls, orientation controls always require at least one datum reference and never control feature location . For planar surfaces, parallelism establishes a 3D tolerance zone bounded by two parallel planes parallel to a datum plane, refines the Rule #1 envelope, must be smaller than the size tolerance, and strictly forbids material condition modifiers. When applied to a feature of size (axis or centerplane), parallelism controls the derived median line (DML) or derived median plane (DMP) , requires a diameter symbol (⌀) for cylindrical zones, permits the Maximum Material Condition ( Ⓜ ) modifier, generates bonus tolerance , and establishes an unyielding virtual condition (VC) boundary ( V C = M M C + t VC = MMC + t V C = MMC + t for pins; V C = M M C − t VC = MMC - t V C = MMC − t for holes).

Fundamental Rules Governing Orientation Controls (ASME Y14.5-2009 Section 6.2 & 6.3)

Orientation tolerancing governs the angular relationship between geometric features and designated datum reference frames. Understanding orientation requires mastering three fundamental GD&T principles that apply uniformly to parallelism, perpendicularity, and angularity.

Rule 1: Orientation Controls ALWAYS Require Datums

Form controls (straightness, flatness, circularity, cylindricity) are intrinsic shapes evaluated in isolation and never reference datums. In stark contrast, orientation represents a relative relationship: a feature cannot be "parallel" or "perpendicular" by itself; it must be parallel or perpendicular to something else .

An orientation feature control frame lacking a datum reference (e.g., [ Parallelism | 0.05 ] ) is an invalid syntax error .

An orientation control requires at least one primary datum reference. It may include secondary or tertiary datums when necessary to constrain additional rotational degrees of freedom.

Rule 2: Orientation Controls NEVER Control Location

One of the most pervasive misconceptions in mechanical design is assuming that parallelism controls the distance between features.

Orientation controls govern angular tilt only. They do NOT locate a feature relative to datums.

When a top surface has a parallelism control to bottom datum A, the feature control frame does not restrict the height of the part. Height (distance from datum A) is controlled exclusively by the size tolerance or by a location control (such as profile or position).

The tolerance zone for planar surface parallelism is free to translate up and down throughout the entire size tolerance band; it is only constrained to remain parallel (tilt = 0° basic) to the datum plane.

Rule 3: The Geometric Tolerance Hierarchy (Form Refinement)

Geometric controls follow a strict nested hierarchy: Size ≥ Location ≥ Orientation ≥ Form \text{Size} \ge \text{Location} \ge \text{Orientation} \ge \text{Form} Size ≥ Location ≥ Orientation ≥ Form

An orientation tolerance automatically refines the form of the controlled feature:

A planar surface parallelism tolerance of 0.10 mm 0.10\text{ mm} 0.10 mm automatically restricts the flatness of that surface to no more than 0.10 mm 0.10\text{ mm} 0.10 mm . A surface cannot exhibit 0.15 mm 0.15\text{ mm} 0.15 mm of bow while remaining inside a 0.10 mm 0.10\text{ mm} 0.10 mm parallelism zone.

Consequently, a surface parallelism tolerance must be less than the total size tolerance . If a plate has a thickness of 20.0 ± 0.2 mm 20.0 \pm 0.2\text{ mm} 20.0 ± 0.2 mm (size tolerance = 0.4 mm 0.4\text{ mm} 0.4 mm ), specifying a surface parallelism of 0.5 mm 0.5\text{ mm} 0.5 mm is redundant and invalid under Rule #1.

An independent flatness control is only necessary if the designer needs the surface form to be refined tighter than its allowable orientation tilt (e.g., parallelism of 0.15 mm 0.15\text{ mm} 0.15 mm with flatness refined to 0.05 mm 0.05\text{ mm} 0.05 mm ). THE GEOMETRIC TOLERANCE HIERARCHY

┌─────────────────────────────────────────────────────────────┐
│ SIZE TOLERANCE (Limits of Size / Rule #1 Envelope) │
│ ┌───────────────────────────────────────────────────────┐ │
│ │ LOCATION CONTROLS (Position, Profile of a Surface) │ │
│ │ ┌─────────────────────────────────────────────────┐ │ │
│ │ │ ORIENTATION (Parallelism, Perpendicularity) │ │ │
│ │ │ ┌───────────────────────────────────────────┐ │ │ │
│ │ │ │ FORM CONTROLS (Flatness, Straightness) │ │ │ │
│ │ │ └───────────────────────────────────────────┘ │ │ │
│ │ └─────────────────────────────────────────────────┘ │ │
│ └───────────────────────────────────────────────────────┘ │
└─────────────────────────────────────────────────────────────┘
Planar Surface Parallelism (ASME Y14.5-2009 Section 6.4.2)

Parallelism is the condition of a surface, centerplane, or axis that is equidistant at all points from a datum plane or datum axis. When applied to a planar surface, parallelism ensures that a functional contact face does not tilt excessively relative to a reference datum plane.

Tolerance Zone Definition

The tolerance zone for planar surface parallelism is a three-dimensional volume bounded by two parallel planes separated by the specified tolerance value t t t :

The two tolerance planes are oriented exactly parallel (0° basic) to the designated datum plane.

The tolerance zone is free to translate along the datum normal vector to contain the actual surface, bounded only by the allowable size limits.

All extracted points of the toleranced surface must lie simultaneously between these two parallel planes.

Drawing Callout & Syntactical Rules

When specifying planar surface parallelism:

The feature control frame is placed with a leader line pointing directly to the physical surface, or attached to an extension line extending from the surface, visibly offset and separated from any size dimension.

No Diameter Symbol (⌀) : Because the tolerance zone consists of two parallel planes, specifying ⌀ is a severe syntax error.

Material Condition Modifiers (Ⓜ / Ⓛ) Strictly Prohibited : A physical planar surface has no feature size and contains no material volume departure. Placing Ⓜ or Ⓛ in a surface parallelism frame is an invalid callout under ASME Y14.5-2009 Section 6.3.1.

Parallelism Applied to Features of Size (ASME Y14.5-2009 Section 6.4.2 & 6.4.2.1)

Section 6.4.2 permits parallelism to be applied to regular features of size , including cylindrical pins, bores, shafts, holes, and non-cylindrical tabs and slots.

Parallelism of an Axis (Cylindrical Feature of Size)

When parallelism is applied to a cylindrical feature of size:

Drawing Placement : The feature control frame is associated directly with the size dimension (placed under the dimension, attached to the dimension line, or attached to the diameter leader).

Controlled Entity : The control applies to the derived median line (DML) (the axis) of the feature, NOT the physical outer surface.

Mandatory Diameter Symbol (⌀) : Because the axis is free to tilt in any radial direction within 360°, the tolerance zone is a cylindrical volume whose axis is parallel to the datum. The tolerance value must be preceded by the diameter symbol (⌀) . Omitting ⌀ specifies two parallel planes, which is only valid if a directional orientation vector is explicitly detailed.

Parallelism of a Centerplane (Non-Cylindrical Feature of Size)

When parallelism is applied to two parallel opposed planar surfaces (such as a keyway slot or mounting tab):

The control applies to the derived median plane (DMP) of the feature of size.

The tolerance zone consists of two parallel planes parallel to the datum plane or datum centerplane.

The diameter symbol (⌀) is prohibited for centerplane controls.

Material Condition Modifiers, Bonus Tolerance, & Virtual Condition

By default under Rule #2 (ASME Y14.5-2009 Section 2.8), all geometric tolerances apply Regardless of Feature Size (RFS) . However, when applied to a feature of size, parallelism may specify the Maximum Material Condition (Ⓜ) or Least Material Condition (Ⓛ) modifier.

When the Ⓜ modifier is specified:

Base Tolerance : The stated tolerance applies only when the feature of size is produced at its Maximum Material Condition (MMC).

Bonus Tolerance : As the actual mating size of the feature departs from MMC toward LMC, bonus tolerance is unlocked on a 1:1 basis: Bonus Tolerance = ∣ Actual Mating Size − MMC ∣ \text{Bonus Tolerance} = |\text{Actual Mating Size} - \text{MMC}| Bonus Tolerance = ∣ Actual Mating Size − MMC ∣ Total Permissible Parallelism = Specified Tolerance + Bonus Tolerance \text{Total Permissible Parallelism} = \text{Specified Tolerance} + \text{Bonus Tolerance} Total Permissible Parallelism = Specified Tolerance + Bonus Tolerance

Virtual Condition (VC) : An invariant worst-case geometric boundary generated by the collective effect of the feature's MMC size and its orientation tolerance at MMC:

For an External Feature of Size (Pin / Shaft / Tab) : V C external = MMC + Parallelism Tolerance at MMC VC_{\text{external}} = \text{MMC} + \text{Parallelism Tolerance at MMC} V C external = MMC + Parallelism Tolerance at MMC

For an Internal Feature of Size (Hole / Bore / Slot) : V C internal = MMC − Parallelism Tolerance at MMC VC_{\text{internal}} = \text{MMC} - \text{Parallelism Tolerance at MMC} V C internal = MMC − Parallelism Tolerance at MMC

Step-by-Step Worked Calculations
Case A: External Guide Pin at MMC
An alignment pin is dimensioned: ∅ 20.00 ± 0.10 mm \varnothing 20.00 \pm 0.10\text{ mm} ∅ 20.00 ± 0.10 mm

[ ∥ | ⌀0.08 Ⓜ | A ] Datum A is a planar mounting surface.

Determine Limits of Size & MMC :

MMC = ∅ 20.10 mm \text{MMC} = \varnothing 20.10\text{ mm} MMC = ∅ 20.10 mm (maximum material / largest pin diameter)

LMC = ∅ 19.90 mm \text{LMC} = \varnothing 19.90\text{ mm} LMC = ∅ 19.90 mm (least material / smallest pin diameter)

Calculate Virtual Condition (VC) : V C = MMC + Parallelism Tolerance = 20.10 + 0.08 = ∅ 20.18 mm VC = \text{MMC} + \text{Parallelism Tolerance} = 20.10 + 0.08 = \varnothing 20.18\text{ mm} V C = MMC + Parallelism Tolerance = 20.10 + 0.08 = ∅ 20.18 mm A functional receiver mating hole of diameter ∅ 20.18 mm \varnothing 20.18\text{ mm} ∅ 20.18 mm oriented parallel to datum A will guarantee assembly.

Evaluate at Actual Produced Sizes :

If produced at MMC ( ∅ 20.10 mm \varnothing 20.10\text{ mm} ∅ 20.10 mm ) : Bonus = 20.10 − 20.10 = 0.00 mm ⟹ Permissible Axis Tilt = ∅ 0.08 mm \text{Bonus} = 20.10 - 20.10 = 0.00\text{ mm} \implies \text{Permissible Axis Tilt} = \varnothing 0.08\text{ mm} Bonus = 20.10 − 20.10 = 0.00 mm ⟹ Permissible Axis Tilt = ∅ 0.08 mm

If produced at ∅ 20.02 mm \varnothing 20.02\text{ mm} ∅ 20.02 mm : Bonus = 20.10 − 20.02 = 0.08 mm ⟹ Permissible Axis Tilt = 0.08 + 0.08 = ∅ 0.16 mm \text{Bonus} = 20.10 - 20.02 = 0.08\text{ mm} \implies \text{Permissible Axis Tilt} = 0.08 + 0.08 = \varnothing 0.16\text{ mm} Bonus = 20.10 − 20.02 = 0.08 mm ⟹ Permissible Axis Tilt = 0.08 + 0.08 = ∅ 0.16 mm

If produced at LMC ( ∅ 19.90 mm \varnothing 19.90\text{ mm} ∅ 19.90 mm ) : Bonus = 20.10 − 19.90 = 0.20 mm ⟹ Permissible Axis Tilt = 0.08 + 0.20 = ∅ 0.28 mm \text{Bonus} = 20.10 - 19.90 = 0.20\text{ mm} \implies \text{Permissible Axis Tilt} = 0.08 + 0.20 = \varnothing 0.28\text{ mm} Bonus = 20.10 − 19.90 = 0.20 mm ⟹ Permissible Axis Tilt = 0.08 + 0.20 = ∅ 0.28 mm

Case B: Internal Bushing Bore at MMC

A guide bushing bore is dimensioned: ∅ 32.00 + 0.15 − 0.00 mm \varnothing 32.00 \begin{matrix} +0.15 \\ -0.00 \end{matrix}\text{ mm} ∅ 32.00 + 0.15 − 0.00 mm

[ ∥ | ⌀0.05 Ⓜ | A ] Datum A is a planar base.

Determine Limits of Size & MMC :

MMC = ∅ 32.00 mm \text{MMC} = \varnothing 32.00\text{ mm} MMC = ∅ 32.00 mm (maximum material / smallest hole diameter)

LMC = ∅ 32.15 mm \text{LMC} = \varnothing 32.15\text{ mm} LMC = ∅ 32.15 mm (least material / largest hole diameter)

Calculate Virtual Condition (VC) : V C = MMC − Parallelism Tolerance = 32.00 − 0.05 = ∅ 31.95 mm VC = \text{MMC} - \text{Parallelism Tolerance} = 32.00 - 0.05 = \varnothing 31.95\text{ mm} V C = MMC − Parallelism Tolerance = 32.00 − 0.05 = ∅ 31.95 mm A functional go-gage pin of diameter ∅ 31.95 mm \varnothing 31.95\text{ mm} ∅ 31.95 mm oriented parallel to datum A represents the virtual condition boundary.

Evaluate at Actual Produced Size ( ∅ 32.10 mm \varnothing 32.10\text{ mm} ∅ 32.10 mm ) :

Bonus = 32.10 − 32.00 = 0.10 mm \text{Bonus} = 32.10 - 32.00 = 0.10\text{ mm} Bonus = 32.10 − 32.00 = 0.10 mm

Total Permissible Axis Tilt = 0.05 + 0.10 = ∅ 0.15 mm \text{Total Permissible Axis Tilt} = 0.05 + 0.10 = \varnothing 0.15\text{ mm} Total Permissible Axis Tilt = 0.05 + 0.10 = ∅ 0.15 mm

Metrology & Inspection Methods for Parallelism

Surface Plate & Dial Test Indicator (Planar Surfaces) :

Setup : Datum feature A is positioned directly in contact with a calibrated granite surface plate (or clamped to a precision angle plate).

Measurement : A dial test indicator mounted on a transfer stand is set to zero on the toleranced surface. The indicator is swept across the entire extent of the surface.

Result : The Full Indicator Movement (FIM) (the difference between maximum and minimum dial readings) represents the parallelism error. The FIM must not exceed the specified tolerance value t t t .

Coordinate Measuring Machine (CMM) :

Points are probed on the datum feature to establish the mathematical datum reference plane.

Points are probed across the toleranced surface or cylindrical feature of size.

The software calculates the maximum distance between two parallel planes (parallel to the datum plane) that enclose all probed surface points, or evaluates the axis tilt relative to the datum.

Functional Gaging (Features of Size at MMC) :

When parallelism is specified at MMC (Ⓜ), a fixed-size functional attribute gage can verify acceptance.

For an external pin, a gage sleeve with an internal diameter manufactured at the Virtual Condition ( V C = MMC + t VC = \text{MMC} + t V C = MMC + t ) oriented parallel to the datum face is used. If the pin fully enters the sleeve while the datum face contacts the gage reference plane, the part is functionally acceptable.

Surface Parallelism vs. Feature of Size Parallelism: Master Comparison Table

Attribute / Parameter Surface Parallelism (ASME Y14.5 §6.4.2) FOS Axis Parallelism (ASME Y14.5 §6.4.2) FOS Centerplane Parallelism (ASME Y14.5 §6.4.2)

Controlled Geometric Entity Physical planar surface points Derived Median Line (DML / Axis) Derived Median Plane (DMP)

Tolerance Zone Geometry Two parallel planes ( t t t ) Cylindrical zone (⌀ t t t ) Two parallel planes ( t t t )

Diameter Symbol (⌀) in FCF Strictly Prohibited Mandatory Strictly Prohibited
Datum References Required Minimum 1 datum Minimum 1 datum Minimum 1 datum
Material Condition (Ⓜ / Ⓛ) Strictly Prohibited Permitted (RFS is default) Permitted (RFS is default)
Bonus Tolerance Possible? No (Constant zone) Yes (If Ⓜ or Ⓛ specified) Yes (If Ⓜ or Ⓛ specified)

Virtual Condition Created? No (Bounded by size limits) Yes : V C = MMC ± t VC = \text{MMC} \pm t V C = MMC ± t Yes : V C = MMC ± t VC = \text{MMC} \pm t V C = MMC ± t

Refines Form Automatically? Yes (Refines surface flatness) Yes (Refines axis straightness) Yes (Refines median plane flatness)

Controls Feature Location? NEVER NEVER NEVER
Inspection Tool Indicator on surface plate / CMM CMM / Functional sleeve gage CMM / Functional blade gage
Common Exam Traps: Parallelism Controls

Trap 1: Believing Parallelism Controls Feature Height or Location : Exam questions often depict a block with thickness 50 ± 0.5 mm 50 \pm 0.5\text{ mm} 50 ± 0.5 mm and a top surface parallelism of 0.1 mm 0.1\text{ mm} 0.1 mm to datum A. Candidates often incorrectly think the top surface must be within 0.1 mm 0.1\text{ mm} 0.1 mm of the 50 mm nominal dimension. Parallelism controls angular tilt only. The height can measure anywhere from 49.5 to 50.5 mm as long as its tilt does not exceed 0.1 mm.

Trap 2: Omitting the Diameter Symbol (⌀) for Axis Parallelism : For a cylindrical pin or hole, the tolerance zone is a cylinder in 3D space. Omitting ⌀ is a major drafting error frequently highlighted on the GDTP Technologist exam.

Trap 3: Specifying Ⓜ or Ⓛ on a Planar Surface Callout : A physical planar surface has no feature size. Any question presenting [ Parallelism | 0.1 Ⓜ | A ] pointing to a planar surface is showing an illegal syntax error .

Trap 4: Inverting the Virtual Condition Sign : For an external feature (pin/tab), V C = MMC + tolerance VC = \text{MMC} + \text{tolerance} V C = MMC + tolerance . For an internal feature (hole/slot), V C = MMC − tolerance VC = \text{MMC} - \text{tolerance} V C = MMC − tolerance . Exam distractors routinely swap these signs.

Trap 5: Believing a Feature Can Pass Parallelism While Failing Flatness : Because the parallelism tolerance zone consists of two parallel planes that contain all surface points, surface flatness error can never exceed the parallelism error. If a surface meets a 0.08 mm 0.08\text{ mm} 0.08 mm parallelism requirement, its flatness is guaranteed to be 0.08 mm 0.08\text{ mm} 0.08 mm or better.